Servomotor mechanism



June 23, 1936.

W. D. GOVE AL SERVOMOTOR MECHANISM 3 Sheets-Sheet 1 Filed Jan. 31, 1935 M m a 5 v. e J/W 1Q gag. I F a (Wm/i4 H R Hm M M m R Q m m 5 u 1 a m :r: HI. L w M w l 7/W W n w & M II II I i l W /7 Jr 6, 47 ,7 a: 4 v 8 Q g Q 3 mm k R w R m5 R June 23, 1936. w p GQVE r L 2,045,559

' SERVOMOTOR MECHANISM 3 Sheets-Sheet 2 Filed Jan. 31', 1935 WW IIII'IIIII. 'Illlllllll W ///l il fl' Patented June 23, 1936 UNITED STATES SERVOMOTOR MECHANISM Winfield 1). cm, Detroit, and John 0. Almen, Royal Oak, Micln, assiznors to General Motors Corporation, Detroit, Mich a corporation of Delaware Application January 31, 1935, Serial No. 4,220

16 Claims.

This invention relates to servo-motor apparatus and particularly to mechanical servo-motor apparatus adapted to respond accurately to and follow up external control eiforts.

Among the several objects of the invention are to secure a high ratio of output force as compared with the effort of control applied to the servomotor mechanism; to provide a compact, high duty servo-motor mechanism; to minimize lost motion and lag; to provide a race-and-roller servo-motor mechanism that automatically reverses the connection of a control member to the roller when the sense of rotation of the race is reversed, in order to impart to the output member a. force in the same sense of direction in response to a given movement of the control *member whether the race be rotating in forward or reverse; to render the race and roller mechanism self-loading so as to increase the traction between rollers and races as the load upon the servomechanism increases, and otherwise to improve the operation of mechanical-servos adapted to follow up with precision the efforts of control.

The objects of the invention are achieved by the combination of a rotatable driven race with rollers, each adapted to be steered in varied paths of travel on the raceway by external control means operative to incline each roller about an axis passing through the roller center and its point of contact with the race, thereby imparting precessional movement and/or bodily travel which is utilized to operate a power output member adapted to be connected to means for accomplishing the work desired. In the construction illustrated the race is a rotating cylinder and the rollers are universally mounted in a cage within the cylinder so that the roller peripheries engage the inner' periphery or raceway of the cylinder, and preferably alsoa freely'fioating central race. The cage is fixedly connected with an output shaft. Means for inclining the rollers in response to external control causes them to tilt about an axis perpendicular to a radial plane including the race axis and the roller center, and also to spiral on the 4 cylinder raceway and thereby move the cage and output shaft in an axial direction. The rollers, in tilting, increase the pressure between races and rollers in proportion to the load on the output member. Restoration of the rollers from an inclined position while spiraling, that is, from positions in which their axes are oblique to the race axis to a position in which their axes are parallel with the race axis, is effected by the connections 55 to the rollers from the device that responds to external control efforts. as will more fully appear in the complete description to follow.

In the drawings, wherein like reference characters indicate like parts throughout the several views, 1

Fig. 1 shows a mechanical servo-motor appara tus according to this invention applied to an infinitely variable speed transmission mechanism for the purpose of changing the position of transmission elements in order to vary the speed ratio; 10

Fig. 2 is a transverse section through a transmission casing exposing, in elevation, a mechanical servo-motor apparatus according to this invention, with the output shaft of the servo-motor operatively connected to transmission mechanism 15 control parts;

Fig. 3 is a longitudinal section on a plane indicated by the line 3-3 of Fig. 2;

Fig. 4 is a transverse sectional view of larger scale, on a plane indicated by the line 4-4 of 20 Fig. 3;

Fig. 5 is a sectional view of larger scale, on a plane indicated by line 55 of Fig. 4;

' Fig. 6 is a sectional view on a plane indicated by line 8-6 of Fig. 4; v 26 Fig. 7 is a perspective view of a roller-inclining and restoring device which embraces each of the rollers of the servo-mechanism;

Fig. 8 illustrates in detail a portion of a cage associated with the power output member, for re- 30 .taining the rollers of the servo mechanism;

Fig. 9 is a diagram showing at the left a roller in a normal position with its axis parallel with the race axis, and at the center and right the same roller in reversed positions of-inclination 35' and opposite senses of rotation.

The invention is disclosed in association with a motor vehicle variable-speed friction transmission mechanism of race and roller type for the purpose of illustrating one useful industrial ap- 40 plication of it. The invention is, however, of general application to mechanisms wherein servomotor actuations that exactly follow up the movements of a control device-starting, operating and stopping, in exact response to manual or other external influence.

In Fig. 1, numeral I 0 indicates a casing that houses a duplex race and roller transmission mechanism of a type fully disclosed in a prior application of Almen and Gove, entitled Control ior toric friction transmission, filed December 20,

1934, SerialNo. 758,394.

A description of the mechanism within the easing, only suflicient to make clear one application 5 of this invention, follows: 4

' shaft consists of axially alined sections 20, 20

adapted to be clutched together to rotate as one,

or unclutched so that they may rotate assepar'ate members. A gear 22 is secured to input shaft section 20' and meshes with a mating gear 80in order to rotate the driving races. Shaft section 20' carries one element ll of a jaw clutch, which is adapted to interlock with a mating element 82 on the hub 80 of a reverse gear 28 slidably splined to input -shaft section 20. Reverse gear may he slid into engagement with a companion gear l0 on the output shaft l0 in order to drive the latter in reverse; or it may be disengaged from gear 48 and moved into neutral position, as shown in Fig. 1, wherein both forward and reverse drive trains are disconnected; or it may be shifted so as to interlock clutch elements N and 82, and thereby connect the forward driving train with the prime mover, such as an engine, not shown. A bevel pinion l0 is secured to the forward end of the output shaft (the left-hand end as viewed in Fig. 1)

from which power may be taken to drive, for example, the traction wheels of a vehicle. The output shaft is rotated during forward driving from gear 22 through gear 00, driving races 0l, 0l, driven races 02, 02*, which are positively connected to the output shaft, and through the intermediate power transmitting rollers 10 in tractive contact with both driving and driven races. The rollers are mounted in carriers 80, each universally pivoted to a frame member I2, or I2, and said carriers may be shifted by control links H, I0, having their outer ends pivoted to the carriers at opposite sides of the roller axes and their inner ends connected to independently movable control collars I2 and 'Il adapted to be actuated by mechanism including master links I8, which are operated by a rocking movement of a control shaft I'I, provided with an arm flxed at each end to which links I0 are connected.

The servo-motor mechanism to which this 'invention particularly relates is shown in Figs. 1 and 2 supported by frame member I2', and

with the servo-power-output member connected to control shaft IIl so as to rock it, in one sense or the other, in response to an external effort applied to the servo-motor mechanism.

As shown best in Fig. 3, a bracket I00, secured to frame member I2, has a supporting and bearing sleeve I02, in which the servo-motor is mounted. A longitudinally bored rotatable member, through which the servo-motor mechanism receives power from input shaft 20, is rotatably mounted in and prevented from axial movement by, the supporting and bearing sleeve I 02. Said power receiving member consists of a tubular shaft I0l within the bearing sleeve; a flange-like member I00 rigid with the tubular shaft I, said member I00 having bevel gear teeth I00 and a castellated rim IIO formed with alternating teeth and notches I I2; and a hollow or tubular race I ll having an internal raceway and equipped at one end with teeth and notches I I0 intercalated with the teeth and notches II2 on the castellated rim I I0. Race I ll is bound in coaxial relation to the other parts ml and I00 of the rotary power receiving member, as by a sheet metal cover Ill surrounding the race and spun down over its ends and over the castellated rim of the member I00. The internal diameter of the cover H8 is a trifle greater than the external diameter of race Ill,

so that the latter may deform slightly without interference of the cover. A bevel pinion I20 secured to the rear end of input shaft section 20 meshes with the teeth I08 on the power receiving member of the servo-motor mechanism.

The described power'receiving member is held against axial movement within and-with respect to the bracket and bearing sleeve I02 by the part I00 at one end (the right hand end as viewed in Fig. 3) which contacts with the adjacent end of sleeve I02, and by a collar I22 that bears against the other end of said sleeve I02, and may be locked in place, as by a snap ring I22 removably seated in a groove in the tubular part I00 of said power receiving member. Whenever the. clutch elements 2l and 82 are engaged and the prime mover coupled to input shaft section 20, the power receiving member, consisting of parts I0'l, I00 and I, are rotating in when it is coupled to shaft section 20, and reversely when it is disconnected from shaft 20 and reverse gears 28 and l8 are in mesh. I In the latter assumed condition, output shaft l0 (carrying gears l0 and 08) rotates clockwise (viewed as in Fig. 2) as do races 02 and 02 keyed to it; intermediate rollers I0 and 10' being now rotated by races 52 and 52", turn races 0l, il and gear 00 counterclockwise, and gear 00 intermeshed with gear 22 rotates the latter clockwise (all as viewed in Fig. 2, from the rear). It will therefore be apparent that during forward driving of the. transmission the power receiving member comprising geared element I00 will be rotating counter-clockwise as viewed from the lower end of the servo-motor mechanism,that is, from the right of Fig. 3,-'-and clockwise during rearward driving. And whenever the prime mover is delivering torque to shaft 20 and the transmission is coupled either in forward or reverse, the power receiving member of the servo-motor device is rotating in one sense orthe reverse. The rotative movement 'of the race Ill may be converted into an axial movement, in either sense, of the power output element I2l of the servo-motor by mechanism now to be described.

- The servo-motor output element I2l consists of a tubular shaft I20 having an enlarged end part fabricated into a roller guiding cage. Said cage comprises the extended circular flange I28 shown integral with tubular part I20, and having a face I00 generally in a plane perpendicular to motor output member for accommodating the power transmission rollers. Cage member I34 has a perforation or bore 0 of the same diameter as the countersink I32 in flange I28, and coaxial with said countersink when the flange I28 and member Ill are riveted together. Member 76 disposed. 120 degrees apart and are separated 60 degrees from the points" I42 in the construction illustrated. The radius of member I34 at points I46 is equal to the radius of flange I 28.

The opposed surfaces of flange I28 and companion star-like member I34 are formed with opposed radial, parti-cylindrical grooves spaced 120 apart. The grooves in one member of the cage are of the same radii struck from the same axisas the opposed grooves in the other member. These grooves are formedin radial lands or elevations in the respective members I28 and I 34. The grooves in member I28 are indicated by numeral I 3| and those in member I34 by numeral I43. In Fig. 8, the face of member I34 shows the radial grooves on the inner surface of member I34, that is, the surface I48, opposed to surface I30 of member I 28.

Power transmission rollers I50 aredisposed in the cage-end of output member I24, as shown most clearly in Figs. 3 to 6. Each roller is equipped with two parti-spherical bosses I52, one

protruding centrally from each face. Thebosses. I52 are preferably surfaces of a hard steel ball pressed into a hole formed axially through the roller. The bosses I52 are glided in the particylindrical grooves I3I and I49 of members I 28 and I34. They are neatly fitted to the grooved surfaces, which may be of the same radius of curvature. Thus each roller may have three degrees of angular motion and may move radially should distortions of the races permit, but is restrained by the grooves from circumferential or tangential movement with respect to the cage.

Rollers I50, of which there are three equally spaced, are in rolling contact with the internal cylindrical raceway of race II4, and with the raceway I56, of a centrally disposed ring-like,

floating race I54. Raceway I56 of floating race I54 may be curved in an axial plane as well as in a plane perpendicular to the axis. The ringlike race I54, is free-floating in any direction; bore I in cage member I34 and countersink I 32 in cage member or flange I28 afford space for movement of the floating race; and as the cen-' tral opening therethrough is of greater diameter than the elements encircled by it, said floating race is supported and its position is determined solely by the three rollers I50 the perimeters of which engage the raceway of said floating race at equiangularly spaced points.

Rollers I50 engage the outer cylindrical race I I4 and the central floating race I54 under initial compression allowed by the elasticity of the materials of which the races and rollers are composed. When in the position indicated in Figs. 3, 5 and 6, in which the roller axes are parallel with the axis of race II4, and no movement is imparted to the output member by the rotation of race I I4 and rollers I50, the elastic deformation due to saidinitial compression is least; but if rollers I 50 be tilted about axes passing through the roller centers and perpendicular to planes including the axis of race II4 and the roller centers, said compression or loading is increased. This increase of compression during tilting is of each roller I50, in a plane including the axis of the roller is greater than the radius of the roller and less than the radius of curvature R" of the inside cylindrical surface-or raceway,-

of outer race I I4; and the radius of curvature R. of the raceway I56 of race I54, in a radial plane, is greater than the radius of curvature R of the periphery of roller I50.v The relations specified are such that when said rollers are transmitting power the pressure between the surfaces of races and rollers increases as the resistance encountered by the output member increases, as will presently appear.

, A limit to the extent of axial movement of the servo-power output member I24 is imposed by sleeve I86 and flange I28 on the'output member in cooperation wlth'the bearing I02 of supporting bracket I00 and the tubular part I04 of the power receiving member. The lower end of sleeve I86 stops downward movement of control member I24 by contact with the upper end of power receiving element I04, while upward movement i of said power output member is stopped when flange, member I28. thereon contacts with the lower 'end of said power receiving element.

As may be perceived clearly by reference to Figs. 4 to '1 and 9, a two arm roller-inclining and restoring device I60 is pivotally and frictionally associated with each roller so that the position of the arms is influenced and determined by the roller during rotation in such manner that, de-

pendent upon the sense of rotation of the roller, one arm or the other is set automatically in such position that its extremity is engaged 'byan externally operated control member to be described.

Each roller-inclining and restoring device I60,

shown separately in Fig. '7, comprises a principal member I62 having a flat part from opposite ends of which projectarms I64, I64 equipped with ball tips I66, and a recurved auxiliary member I68 parallel with the flat portion of the principal member I62. A circular hole I69 in the flat part of member I 62, and a coaxial semi-circular notch I12 in the member I68, admit the spherical bosses I52 of the roller I50. Device I60 is shown as formed of elastic sheet metal with the member I60 spaced from the principal member I62 in such relation that when sprung over the roller and the bosses the device may pivot on the bosses and At its upper end,--the end opposite that which carries the cage and rollers described-the tubular shaft I26 of servo output member I24 is con nected toone arm I10 of hell crank lever fixed to the control shaft 11 near the rear end, the

, other arm I13 of said lever having a pivotal connection with the rearward master link 15, as

indicated in Figs. 1 and 2. Another arm I13 1m: 15, as indicatedin Fig. 1.-

A pin I14 having a spheroidal projecting part I16 is riveted or otherwise secured in the end of arm I10. The spheroidal projection I16 of the 1 pin fits within a cylindrical hole I16 in collar I60, which is sleeved over and keyed to tubular shaft I26, as clearly shown in Fig. 3. Collar I00 isprevented from moving toward the upper end of shaft I26 by a nut I62 associated with a lock washer I84 of suitable type. It is prevented from moving toward the cage end by spacing sleeve I66 which engages a shoulder I66 on shaft I26. The control element is free to move angularly about its axis to follow the arcuate movement of arm I10 without disturbing the operation ofraces and rollers. Hence endwise right line movement of shaft I26 may move the arm I12 angularly by reason of the connection shown, without the interposition of linkage, and so rock the control shaft 'II.

The cooperating power receiving and power transmitting elements of the servo-motor mechanism assembled in their proper relations having been described, there remain to be described the means whereby the power of said mechanism maybe made effective or ineffective and otherwise controlledv either automatically, as by a governor, or by the muscular efforts of an operator,

. or both.

External control effort may be transmitted to the rollers I in order to incline them through an internal control member consisting of ashaft I90 ,slidable within tubular output shaft I26 and a control head I92 secured to the lower end of shaft I90. below the roller cage. Shaft I90 is guided within tubular output shaft I26 by bearing enlargements I94. The upper end (the lefthand end in Fig. 3) projects from the tubular input shaft. To this end an arm I96 is secured in any suitable way. as by riveting. Arm I96 extends from the shaft at right angles, but the remote end is disposed substantially parallel with said shaft, as shown in Fig. 3, and is perforated to receive the spheroidal head I96 of a pin 200 riveted or otherwise secured to one arm 202 of a two armed rock-member freely movable angularly about the end of rockshaft 'I'I, rearward of the arms "0 and I12, which are fixed to said rockshaft (see Figs. 1 and 2). The other arm 204 of the two-armed rock-member that is er with race II4.

freely movable about the axis of shaft 11 has a crankpin 206 to which external force may be applied to move the slidablecontrol member axially. The force applied to crankpi-n 206 may be from the muscular efiort of an operator or from the speed responsive orother automatic movement of a governor or a combination of both.. In Fig. 1, there is shown a link 208, universally jointed to the pin 206 on arm 204 at one end and at the other end to the bell crank lever 2I0, the latter being under the joint control of the operator and a speed responsive governor through mechanical linkage not fully shown since the particular external control connections utilized are-not a partof the invention claimed.

The control head I92 is provided with a relatvely long hub 2I2 the upper end of which abuts against one of the bearing enlargements I94 on shaft I90.passing through the bore of floating race I54, as shown in Fig. 3-while the lower end abuts against a lock washer 2I4 backed by a nut 216; and thus the said control head is positioned on shaft I90 and held against relative endwise movement with respect to the said shaft.

I-lead I92 has a peripheral flange 2I6 projecting upward (to the left as seen in Fig. 3) toward the rollers I and overhanging or telescoping the member I64 of the roller cage, as shown in Figs. 3, 5 and 6. A circular groove 220 is formed in the inner surface of flange '2I6. This groove is preferably rectangular in cross section with chamfered edges. Groove 220 is of a depth from the chamfers to the bottom somewhat greater than half the diameter of the spherical tips I66 on the arms I64, I64 of rollen-inclining and restoring device I60. One-or the other of said spherical tips I66 on each device I60 is disposed in groove 220 .during rotation of the rollers, as indicated in Fig. 4. If race II4I rotates inthe direction of the arrow, that is, clockwise (if viewed from the upper end as in Fig. 4) as in forward :driving, the rollers also rotate clockwise, and therefore that arm of each roller-inclining .and restoring device I60, which is in what may be referred to as the approaching quadrant with respect to race I I4, will, due to the friction between device I60 and the faces of the 26 roller, be moved into groove 220, and the other arm (in the retreating quadrant) moved away from it. The chamfered edges of groove 220 pilot the spherical tips I66 into the groove, and since the rectangular-in-section portion of the groove is deeper than one half the diameter of the spherical tips. axial movement of the control head I92 pressing against the end of one arm only will positively incline each member I60 and with it roller I50 about an axis including the roller center and the point of contact of the roll- When inclined as described, the rollers will spiral on race H4 in an upward or downward progressing spiral, depending upon whether the control head I92 has been moved upward or downward and independent of the sense of rotation of the race. During forward driving when race II4 rotates, clockwise viewed from the upper end, as in Fig. 4, or counterclockwise viewed from the lower end as in Fig. 5, the tips I66 of arms I64 will be engaged in groove 220 of head I92, but when the race I I4 is reversely rotating tips of arms I64 will be so engaged.

As illustrated in Fig. 9, a downward movement of head I92 when race H4 is rotating counterclockwise (now for convenience viewing it from the lower end) as in forward driving, will incline the rollers (as illustrated in the middle diagram of Fig. 9) so that they tend to spiral toward the lower end of the servo-mechanism and move the servo-output member downward, thus rocking control shaft 11 clockwise (as viewed in Fig. 2 from the rear) and, through links I5, collars I2 and links I3, inclining rollers l0, 10' so that they will spiral toward highspeed ratio position. Movement of head I92 upward will cause the rollers I60 to spiral upward thus moving the servo-output member upward and so rocking control shaft I'I counterclockwise (as viewed from the rear) and shifting rollers I0, 10" to a lower speed ratio position. I

In case the race II4 be rotating clockwise, (viewed from the lower end) that is, reversely, the arms I64 will be engaged in groove 220 of the control head I92 and arms I64 disengaged. Then, downward movement of control head will incline rollers I60 as indicated in the right hand diagram of Fig. 9. Inasmuch as race H4 is now rotating reversely or clockwise, the rollers will spiral in a downward direction, moving servo-output member, downward, rocking shaft 11 clockwise (as viewed from the rear). And as the direction of rotation of races 64, 64 and 52, 52

has been reversed and the rollers are now being driven by races 52 and 52, the inclination imparted to them through links 15, reverse collars 14 and links II will cause them to spiral outward on races 64, 64 and inward on races 52, 52 to the same roller position as in high speed ratio forward. A movement of control member upward while race II 4 is rotating reversely (clockwise) will incline the rollers I50 oppositely causing them to spiral upward, thus moving servooutput member upward rocking shaft 1'! counterclockwise (as viewed in Fig. 2) and shifting rollers 10, I0 oppositely so that they assume a speed ratio position in reverse, which is the same as the low speed ratio position of the rollers in forward driving.

In order to limit the amplitude .of endwise movement of the internal control member, one adjustable stop, (for limiting upward movement) comprising a threaded-pin 222 is arranged in a threaded hole through an arm 224 projecting from the bearing bracket that is fixed to frame member I2 for supporting shaft 11, and another fixed stop 226 (for limiting downward movement) is formed on the other side of said arm 224. Two stop lugs 228 and 230, integral with the twoarmed rock member having the arms 202 and 204, cooperate with said stops mounted on the bearing bracket. Lug 228 is adapted to contact with the end of the threaded pin 222 to limit the upward movement of the internal control member. An adjustable threaded pin 232 in stop lug 230, is adapted to contact with said fixed stop rotation, or the reverse thereof. While pinion I20 is rotating counterclockwise (as viewed in Fig. 2)

which has been herein indicated as the direction I of rotation during forward driving, the power receiving member including race. H4 is rotating counterclockwise as viewed from the right of Fig. 3. The rollers I50 are being rotated by the outer race H4 with their axes parallel with the axes of the race and with the peripheries in rolling contact with the raceways of said outer race H4 and floating race I54. In this position no movement is imparted to the power output member of the servo-mechanism. It is the position automatically assumed by the rollers when the internal control member I90, I92 is at rest.

If a governing force is applied to internal control member I sufficient to move it and head I92 axially, the rollers I50'wili be inclined in a direction to cause the power output member to follow the control member. Assuming the rotation of race I I4 to be counterclockwise (viewed from its lower end) as in forward driving, and head I92 to have been moved downward, rollers I52 will be inclined as indicated in the middle diagram of Fig. 9.. Inclination in this sense tends to bring about tilting, and in so doing to bring that part of the roller which contacts with race H4 nearer the lower end of the race, or nearer the right-hand end as viewed in Fig. 6, than that part of the roller which engages floating race I54, or than the center of the roller. This tilting occurs because of the resistance to endwise movement of the power output shaft due to the load 5 upon its upper end causing the rollers to pivot around the centers ofthe bosses I52 on cage element I34. In so tilting the rollers are squeezed more tightly between the races I I4 and I54 by reason of the arcs of curvature and relationship 10 between the races and rollers that have been described, thus increasing the degree of traction between races and rollers. The roller bosses I52 in contact with cage element I34 6f the power output member transmit the bodily movement of 15 the rollers, due to their described inclination, to the power output member tending to move it downward, or to the right, as viewed in Fig. 3, thus rocking shaft II in a direction to shift the transmission rollers to a higher speed ratio po- 20 s on.

While the internal control member comprising control head I 92 is being shifted downward as indicated in the middle diagram of Fig. 9, the rollers contemporaneously spiral downward on 25 race H4 and in so doing, after the control member comes to rest/becomes restored to the normal position as indicated in Figs. 5 and 6 and in the left-hand diagram of Fig. 9. This restoring movement, as willbe obvious upon inspection of 30 the diagram, is brought about by the downward right line movement of the center of each roller while the ball tip I66 of the arm I64 of device I60 is held from downward movement and pivots in groove 220,0f head I92. As the roller moves 35 downward the angle its center plane of rotation makes with a plane normal to the race axis, or that which its axis of rotation makes with the race axis, lessens until the angle becomes zero. The rollersare then in the normal position from which they have no tendency to depart until they are again inclined by an axial movement of the internal control member. It is apparent that the extent of movement of the servo-power output shaft is proportional to the extent of movement 45 of the control member and in the same direction. An upward movement of the control member will produce an inclination of the rollers the'reverse of that shown in the middle diagram of Fig. 9, and an upward movement of the power 50 output member. I

If the sense of rotation of the mechanism is reversed, the ball tip I66 of arm I64 of each roller-embracing device I60 will be moved into groove 220 of head I92 as indicated by dotted 5 line illustration of one of the devices I60, in Fig. 4, and by the full line illustration in the right hand diagram of Fig. 9. As the direction of rotation is now reversed and also the inclination of the roller is reversed, whencontrol member is moved downward it is clear the rollers will spiral downward until restoration has occurred, in the same manner as has been described with reference to I forward driving as indicated in the middle diatent.

We claim: 1. The combination in a servo-motor mechanism of an outer hollow race having an internal friction surface, a plurality of-rollers in rolling engagement with said internal friction surface, an inner race concentricwlth said outer race the external surface of which is in frictional engagement with said rollers, means for applying power to rotate one of said races, an axially movable power output member: in which the rollers are inclinably mounted, and control means adapted to incline the rollers about axes passing through their centers and the points of contact with the races. A a

2. A combination as defined in claim 1 in which one of the races is a freely floating race.

3. A combination as defined in claim 1 in which the outer race is rotated by power means.

' cally with respect to the axis of rotation of the 4. A combination as defined in claim 1 in which the outer race is rotated by power means and the inner race floats freely.

5. A combination as definedin claim 1 in which the rollers are elastically compressed between the outer and inner races.

6. A combination as defined in claim 1 in which the rollers are universally mounted in the output member and-elastically compressed between the races, and the races and rollers are formed of relative contours and dimensions effecting an increase of pressure between races and rollers during tilting of the rollers about an axis that passes through the roller center and is perpendicular to a radial plane including the race axis and the roller center.

7. A combination as defined in claim 1 in which the rollers are universally mounted in the power output member, the roller treads are curved in a radial plane, and in which one of the races is equipped with a plain cylindrical raceway and the other with a raceway concave in a radial plane, the radius of curvature in a radial plane of the concave raceway being longer than the radius of curvature in a radial plane of the roller tread.

8. A combination as defined in claim 1 with stop means to limit the range of movement of the power output member.

9. In a servo-motor mechanism the combination of a rotatable hollow power receiving member and means for driving it, said power receiving:

member comprising a race having an internal raceway, a race concentrically disposed within the raceway of the power receiving member, a power output member extending axially through said power receiving -member, rollers rotatably mounted in said power output member and free to incline therein about axes passing through their centers and points of contact with said races, and externally operable control means adapted to hold the rollers tracking in circular paths on the raceways or to incline them so as to track in spiral paths on the raceways, said control means comprising an axially movable member connected with said rollers.

10. In a servo-motor mechanism the combination of a rotatable hollow power receiving member comprising an outer race having an internal cylindrical raceway, an inner race concentrically disposed within said cylindrical raceway, and having a raceway concaved ina radial plane, a power output member extending axially through said power receiving member, rollers universally pivoted in said power output member and in rolling contact with said races, the treads of said rollersbeingcurvedinaradial planeonaradius roller, said device bearing frictionally on the is.

roller and having oppositely extending arms, and means on the control member arranged to enuse either arm.

12. A combination as defined in claim 11 in which the control member is equipped with a 20 head having a groove disposed in position to receive the end of one arm or the other of the roller inclining device dependent upon the sense of rotation of the roller.

13. A combination as defined in claim 11 in 25 which the axially movable control member comprises a head having a fiange provided with an annular internal groove normally overhanging the ends of the arms of the roller inclining device.

14. In race and rollermechanism of the class described, a clip-like roller-incliningdevice composed of elastic material having two members adapted to receive a roller between them and bear frictionally upon the faces thereof, means 35 to support the device so that it may pivot about the axis of rotation of the roller, arms extending oppositely from one of the members, said arms having ends adapted to be selectively engaged by a control member. 40

15. A roller having a spherical boss projecting centrally from each face of the roller, a clip-like roller-incliningdevice, consisting of two elastic members having registering bearing openings fittingover the bosses, one of said members hav- 45 ing oppositely projecting arms the end of one 1 or the other of which is adapted to be selectively engaged by a control member.

. 18. In a servo-motor mechanism the combination of a reversible rotatable power receiving member having an axial opening therethrough and .a race, a race concentric therewith, a longitudinally perforated .power output member movable axially in the opening of the power receiving member, said power output member having acage with spaced members; rollers mounted with three degrees of freedom in said cage, means for preventing angular movement of the rollers about the center of said cage; a roller inclining device in frictionalengagement with each roller 60 and tending to rotate with the roller; arms extending oppositely from said device; a control member axially movable within the power output member, said control'member having a head provided with a groove arranged in position to re- 5 ceive the end of one or the other of said arms depending on the sense of rotation of-the roller. 

